Transcript Engineering Graphics

Mechanics of Machines
Dr. Mohammad Kilani
Class 8
GEAR TRAINS
Introduction
 A gear train is any
collection of two or
more meshing
gears.
 Gear trains are
found in
automobiles,
automated
machines and
numerous other
applications
Simple Gear Trains
 A simple gear train is one in which
each shaft carries only one gear.
 The velocity ratio (sometimes
called train ratio) of this gearset is
found by:
 N  N   N 
 N 
mV    2   3   n1     2 
 N 3  N 4   N n1 
 Nn 
 The sign depends on the total
number of gears in the gearset. It
is positive when the total number is
n-1 is odd and negative when the
n-1 is even.
Simple Gear Trains
 A single gearset is usually
limited to a ratio of about 10:1.
A single gearset will become
very large, expensive, and hard
to package above that ratio if
the pinion is kept above the
minimum numbers of teeth
needed to avoid interference.
 Simple gear trains are
sometimes used to avoid
violating the minimum number
of teeth interference rule,
which could happen if the
input gear meshes directly with
the output gear.
 N  N   N 
 N 
mV    2   3   n1     2 
 N 3  N 4   N n1 
 Nn 
Simple Gear Trains
 It is common practice to insert a single
idler gear to change direction, but more
than one idler is superfluous. There is
little justification for designing a gear train
as is shown in the figure.
 lf the need is to get a larger train ratio
than can be obtained with a single gearset,
the simple train will only function as a
method of moving the location of the
output shaft of the gear set to another
location.
 If the need is to connect two shafts that
are far apart, a simple train of many gears
could be used but will be more expensive
than a chain or belt drive for the same
application. Most gears are not cheap.
 N  N   N 
 N 
mV    2   3   n1     2 
 N 3  N 4   N n1 
 Nn 
Compound Gear Trains
 To get a train ratio of greater than
about 10:1 with spur, helical, or
bevel gears (or any combination
thereof) it is necessary to use a
compound train. A compound train
is one in which at least one shaft
carries more than one gear.
 The figure shows a compound train
of four gears, two of which, gears 3
and 4, are fixed on the same shaft
and thus have the same angular
velocity. The train ratio is:
mV 
5  3  5 
   
2  2  4 
 N  N 
mV    2   4 
 N 3  N 5 
Compound Gear Trains
 The expression above can be
generalized to:
mV  
Product of number teeth of driver gears
Product of number teeth of driven gears
Example 1
 If presented with a completed design of a compound gear train, it is a
trivial task to determine the train ratio. It is not so simple to do the
inverse, namely, design a compound train for a specified train ratio
Example 1
 The first step is to determine how many
stages, or gearsets, are necessary. Simplicity
is the mark of good design, so try the
smallest possibility first. Take the square root
of 180, which is 13.416. So, two stages each
of that ratio will give approximately 180:1.
 However, this is larger than our design limit
of 10:1 for each stage, so try three stages.
The cube root of 180 is 5.646, well within 10,
so three stages will do.
Example 1
 If we can find some integer
ratio of gear teeth which
will yield 5.646:1, we can
simply use three of them to
design our gearbox.
 Using a lower limit of 12
teeth for the pinion and
trying several possibilities
we get the gearsets shown
in the Table as possibilities.
Example 1
 The number of gear teeth must be an integer. The
closest to an integer in the Table is the 79.05 result.
Thus a 79:14 gearset comes closest to the desired ratio.
 Applying this ratio to all three stages will yield a train
ratio of (79114)3 = 179.68:1 , which is within 0.2% of
180:1 . This may be an acceptable solution provided
that the gearbox is not being used in a timing
application. If the purpose of this gearbox is to step
down the motor speed for a crane hoist, for example,
an approximate ratio will be adequate
Example 1
 Many gearboxes are used in production
machinery to drive camshafts or linkages
from a master driveshaft and must have the
exact ratio needed or else the driven device
will eventually get out of phase with the rest
of the machine.
 If that were the case in this example, then
the solution found above would not be good
enough. We will need to redesign it for
exactly 180:1.
Example 1
 Since our overall train ratio is an integer, it will
be simplest to look for integer gearset ratios.
Thus we need three integer factors of 180. The
first solution above gives us a reasonable
starting point in the cube root of 180, which is
5.65. If we round this up (or down) to an integer,
we may be able to find a suitable combination.
 Two compounded stages of 6: I together give
36: I . Dividing 180 by 36 gives 5. Thus the stages
shown in the Table provide one possible exact
solution.
Reverted Compound Gear Trains
 In some cases, such as
automobile transmissions,
it is desirable or even
necessary to have the
output shaft con centric
with the input shaft. This
is referred to as "reverting
the train"or "bringing it
back onto itself."
 The design of a reverted
compound train is more
complicated because of
the additional constraint
that the center distances
of the stages must be
equal.
Reverted Compound Gear Trains
 the equal center
distances constraint can
be expressed in terms of
their pitch radii, pitch
diameters, or numbers
of teeth
r2  r3  r4  r5
d 2  d3  d 4  d5
N 2  N3  N 4  N5
Example 2
Example 2
 Though it is not at all necessary to have integer gearset ratios in a
compound train (only integer tooth numbers), if the train ratio is an
integer, it is easier to design with integer ratio gear sets.
 The square root of 18 is 4.2426, well within our 10:1 limitation. So
two stages will suffice in this gearbox.
Example 2
 If we could form two identical stages, each
with a ratio equal to the square root of the
overall train ratio, the train would be
reverted by default. Table 9-8 shows that
there are no reasonable combinations of
tooth ratios which will give the exact
square root needed. Moreover, this
square root is not a rational number, so we
cannot get an exact solution by this
approach
Example 2
 Instead, let's factor the train ratio. All
numbers in the factors 9 x 2 and 6 x 3 are
less than I 0, so they are acceptable on that
basis. It is probably better to have the
ratios of the two stages closer in value to
one another for packaging reasons, so the
6 X 3 choice will be tried
Example 2
 In addition, we have the constraint that the
center distances of the stages must be
equal.
N 2  N 3  N 4  N5  K
N2 1
 , N3  6N2
N3 6
N2  6N2  7 N2  K
N 4  3N 4  4 N 4  K
N4 1
 , N 5  3N 4
N5 3
Example 2
 The parameter K must be set to at least the
lowest multiple of 7 and 4, which is 28. This
yields N2 = 4 teeth and N4 = 7 teeth.
 Since a four-tooth gear will have unacceptable
undercutting, we need to increase K sufficiently
to make N2 = 12. This results in K = 84. This
results in the following viable solution:
N 2  12, N 3  72
N 4  21, N 5  63
EPICYCLIC OR PLANETARY GEAR TRAINS
 The conventional gear
trains described in the
previous sections are all
one-degree-of-freedom
(DOF) devices.
 Another class of gear
train has wide
application, the epicyclic
or planetary train. This is
a two-DOF device. Two
inputs are needed to
obtain a predictable
output.
EPICYCLIC OR PLANETARY GEAR TRAINS
 In some cases, such as the
automotive differential, one
input is provided (the driveshaft)
and two frictionally coupled
outputs are obtained (the two
driving wheels).
 In other applications such as
automatic transmissions, aircraft
engine to propeller reductions,
and in-hub bicycle
transmissions, two inputs are
provided (one usually being a
zero velocity, i.e., a fixed gear),
and one controlled output
results.
EPICYCLIC OR PLANETARY GEAR TRAINS
 In the conventional, one-DOF
gearset, link I is immobilized
as the ground link. The same
gearset could have link 1 free
to rotate as an arm which
connects the two gears. Now
only the joint 02 is grounded
and the system DOF = 2.
 This has become an epicyclic
train with a sun gear and a
planet gear orbiting around
the sun, held in orbit by the
arm.
EPICYCLIC OR PLANETARY GEAR TRAINS
 Two inputs are required in a
planetary gear train. Typically, the
arm and the sun gear will each be
driven in some direction at some
velocity. In many cases, one of
these inputs will be zero velocity,
i.e., a brake applied to either the
arm or the sun gear.
 Note that a zero velocity input to
the arm merely makes a
conventional train out of the
epicyclic train. Thus the
conventional gear train may be
considered a special case of the
more general epicyclic train, in
which its arm is held stationary.
EPICYCLIC OR PLANETARY GEAR TRAINS
 In this simple example of an
epicyclic train, the only gear left to
take an output from, after putting
inputs to sun and arm, is the planet.
It is a bit difficult to get a usable
output from this orbiting gear as its
pivot is moving.
 A more useful configuration is one
in which a ring gear has been
added. This ring gear meshes with
the planet and pivots at O2, so it
can be easily tapped as the output
member. Most planetary trains will
be arranged with ring gears to bring
the planetary motion back to a
grounded pivot.
EPICYCLIC OR PLANETARY GEAR TRAINS
 In this configuration, the sun gear, ring gear, and arm are all brought out
as concentric hollow shafts so that each can be accessed to tap its
angular velocity and torque either as an input or an output.
EPICYCLIC OR PLANETARY GEAR TRAINS
 Epicyclic trains come in
many varieties. Levai
catalogued 12 possible
types of basic epicyclic
trains.
 These basic trains can
be connected together
to create a larger
number of trains having
more degrees of
freedom. This is done,
for example, in
automotive automatic
transmissions.
EPICYCLIC OR PLANETARY GEAR TRAINS
 Epicyclic trains have several
advantages over conventional
trains among which are higher
train ratios in smaller packages,
reversion by default, and
simultaneous, concentric,
bidirectional outputs available
from a single unidirectional
input.
 These features make planetary
trains popular as automatic
transmissions in automobiles
and trucks, etc.
EPICYCLIC OR PLANETARY GEAR TRAINS
 To determine the speed ratios of a
planetary train, we observe that since
the gears are rotating with respect to
the arm and the arm itself has motion,
we have a velocity difference problem.
 Rewriting the velocity difference
equation in terms of angular velocities
relative to the arm, the velocities in an
epicyclic train can be determined.
This requires that the tooth numbers
and two input conditions are known.
gear arm  gear  arm
L  arm
N
 F R
F  arm
NL
EPICYCLIC OR PLANETARY GEAR TRAINS
 Let ωF represent the angular velocity of
the first gear in the train (chosen at either
end), and ωL represent the angular
velocity of the last gear in the train (at the
other end).
 Writing the equation for the first gear in
and for the last gear in the system, and
dividing the second equation by the first
we get
L  arm
NF

R
F  arm
NL
F arm  F  arm
L arm  L  arm
EPICYCLIC OR PLANETARY GEAR TRAINS
 The velocity difference formula can be
solved directly for the train ratio. We can
rearrange the formula to solve for the
velocity difference term. Then, let ωF
represent the angular velocity of the first
gear in the train (chosen at either end),
and ωL represent the angular velocity of
the last gear in the train (at the other
end).
 Writing the equation for the first gear in
and for the last gear in the system, and
dividing the second equation by the first
we get
L  arm
NF

R
F  arm
NL
F arm  F  arm
L arm  L  arm
FERGUSON'S PARADOX
 The Ferguson's paradox is a compound epicyclic train with one 20-tooth
planet gear (gear 5) carried on the arm and meshing simultaneously with
three sun gears. These sun gears have l00 teeth (gear 2), 99 teeth (gear 3),
and 101 teeth (gear 4), respectively.
FERGUSON'S PARADOX
 The center distances
between all sun gears and
the planet are the same
despite the slightly different
pitch diameters of each sun
gear.
 This is possible because of
the properties of the
involute tooth form. Each
sun gear will run smoothly
with the planet gear. Each
gearset will have a slightly
different pressure angle.
Example 4
Example 4
L  arm
N
 F R
F  arm
NL
Sun gear #2 with sun gear #3
3  arm
N
100
 2 
2  arm
N3
99
3  100
100
 100
99
3  1.01 rpm

Sun gear #2 with sun gear #4
4  arm
N
100
 2 
2  arm
N4
101
4  100
100
 100
101
4  0.99 rpm

FERGUSON'S PARADOX
 This result accounts for the use of the word
paradox to describe this train. Not only do we get
a much larger ratio (100:1) than we could from a
conventional train with gears of 100 and 20 teeth,
but we have our choice of output directions.
 Automotive automatic transmissions use
compound planetary trains, which are always in
mesh, and which give different ratio forward
speeds, plus reverse, by simply engaging and
disengaging brakes on different members of the
train. The brake provides zero velocity input to
one train member. The other input is from the
engine. The output is thus modified by the
application of these internal brakes in the
transmission according to the selection of the
operator (Park, Reverse, Neutral, Drive, etc.).
L  arm
N
 F R
F  arm
NL
Sun gear #2 with sun gear #3
3  arm
N
100
 2 
2  arm
N3
99
3  100
100
 100
99
3  1.01 rpm

Sun gear #2 with sun gear #4
4  arm
N
100
 2 
2  arm
N4
101
4  100
100
 100
101
4  0.99 rpm

BEVEL-GEAR EPICYCLIC TRAINS
 The bevel-gear train
shown is called
Humpage's reduction gear.
Bevel-gear epicyclic trains
are used quite frequently
and their analysis may be
carried out as spur-gear
epicyclic trains.
L  arm
N
 F R
F  arm
NL
Sun gear #2 with sun gear #6
6  arm
N  N5
20  24
 2

 0.245
2  arm
N4  N6
56  35